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ORIGINAL ARTICLE
Three-dimensional stability lobe and maximum material
removal rate in end milling of thin-walled plate
Aijun Tang & Zhanqiang Liu
Received: 9 May 2008 /Accepted: 1 August 2008 /Published online: 26 August 2008# Springer-Verlag London Limited 2008
Abstract Chatter phenomenon often occurs during end
milling of thin-walled plate and becomes a commonlimitation to achieve high productivity and part quality.
For the purpose of chatter avoidance, the optimal selection
of the axial and radial depth of cut, which are decisive
primary parameters in the maximum material removal rate,
is required. This paper studies the machining stability in
milling of the thin-walled plate and develops a three-
dimensional lobe diagram of the spindle speed, axial, and
radial depth of cut. Through the three-dimensional lobe, it
is possible to choose the appropriate cutting parameters
according to the dynamic behavior of the chatter system.
Moreover, this paper studies the maximum material
removal rate at the condition of optimal pairs of the axial
and radial depth of cutting.
Keywords Chatter. Three-dimensional stability lobe .
Maximum material removal rate . Thin-walled plate
1 Introduction
With the development of high-speed cutting technology,
many aircraft parts are composed of monolithic components
to form ribs and thin-walled plates. Due to the large area
and low rigidity, the thin-walled plates are always machined
in numerical-control end-milling processes. At the high
removal rate conditions, the milling of thin-walled plate
leads a lot of dynamic and static problems consecutively.
The main dynamic problem is the self-excited vibration
called regenerative chatter. Due to the regenerative chatter,
the cutting thickness is changed with time, which leads tothe dynamic cutting force. Therefore, chatter is one of the
major limitations on high productivity and part quality even
for high-speed and high-precision milling machines.
In workshops, machine tool operators often select
conservative cutting parameters to avoid chatter. Moreover,
in some cases, additional manual operations are required to
clean chatter marks left on the part surface. The studies on
chatter can go back to the 1950s with Tobias [1], Tlusty and
Polacek [2], and Merrit [3], who explained the regenerative
chatter in orthogonal cutting and developed the two-
dimensional stability lobe theory. The two-dimensional
stability lobe theory deals with the stability of solutions
for dynamical cutting systems, which usually stands for the
spindle speed and axial depth. As a function of these two
cutting parameters, the border between a stable cut (i.e.,
chatter-free) and an unstable one (i.e., with chatter) can be
visualized in a chart called stability lobes diagram (SLD).
In the middle of the 1990s, Altintas [4] presented an
analytical form of the stability lobe theory for milling. Both
of these stability lobe theories can help to select the
appropriate cutting parameters of the spindle speed and
axial depth to avoid chatter in machining processes.
In the end milling of thin-walled plates, due to the
change of cutting position, mass and stiffness of cutting
system, and other factors, the two-dimensional stability
lobe diagram sometimes is not comprehensive to describe
the stability of chatter system. Therefore, several researches
on the three-dimensional stability lobe diagram of chatter
system have then been done and achieved some develop-
ments, such as that of Vincent Thevenot et al. who
introduced the dynamical behavior variation of the part
with respect to the tool position in order to determine
optimal cutting conditions during the machining process.
Int J Adv Manuf Technol (2009) 43:3339
DOI 10.1007/s00170-008-1695-y
A. Tang (*) : Z. LiuSchool of Mechanical Engineering, Shandong University,
Jinan, Shandong Province, China
e-mail: [email protected]
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Accordingly, they constructed a three-dimensional stability
lobe diagram of the spindle speed, axial depth, and tool
position with a constant radial depth [5]. U. Bravo and S.
Herranz considered the dynamic parameters variation of the
workpiece along the milling process of the thin-walled plate
as both mass and rigidity were reduced. Sequentially, they
developed a three-dimensional lobe diagram that based on
the relative movement of the chatter systems to cover all theintermediate stages of machining the walls [6, 7]. Tony L.
Schmitz considered the change of system dynamics with
the tool overhang length and developed the three-
dimensional lobe diagram of the spindle speed, axial
depth, and tool overhang length [8].
Material removal rate (MRR) is a critical parameter for
describing the machining process productivity at the
condition of ensuring the quality. MRR in end milling is
proportional to the spindle speed, the axial and radial depth
of cut, the feed per revolution per tooth, and the number of
cutting teeth. Therefore, in order to improve the machining
efficiency, this paper studies the three-dimensional stabilityin milling of the thin-walled plate and develops a three-
dimensional lobe diagram of the spindle speed, and axial
and radial depth of cut. According to the developed three-
dimensional lobe diagram, one can select the appropriate
cutting parameters to avoid chatter at the condition of
ensuring the maximum MRR. The main flow chart of this
research is shown in Fig. 1.
2 Mathematic models of three-dimensional stability lobe
This study is mainly based on the work of Altintas and
Budak [4], and pays more attention on the end milling of
thin-walled plates. Predicting the dynamic behavior for the
chatter system requires a cutting force model, a structural
response model, and a solution procedure.
For simplification, it applies the following assumptions
for the mathematic models of three-dimensional stability of
thin-walled plate:
1. The workpiece is a thin, isotropic, and cantilever plate.
2. The tool is much more rigid than the workpiece.
Therefore, the workpiece can be considered as a
flexible body and can then be modeled as a single
significant mode of vibration
3. The variation of dynamic parameters due to the
material removal is neglected.
4. The end-milling process is up milling, as shown in
Fig. 2.
5. The deflection at different locations of the workpiece is
neglected.
2.1 Mechanical model
According to the assumption 1, the workpiece is modeled
as a thin, isotropic plate, as shown in Fig. 3. I t is
assumed to be clamped at one end, free along the two
parallel sides, and is subjected to the cutting force of the
cutter. It is also assumed that the interactions between the
cutter and the workpiece could be approximately repre-
sented by a cutting region with stiffness k and damping
coefficient c as shown in Fig. 4. The cutter is represented
by a rigid impactor. When the cutter impinges upon thecutting region, the workpiece experiences additional
elastic and damping forces proportional to the cutting
volume.
1. The axial stability limit and spindle speed
In order to analyze easily, the dynamic model in Fig. 4
can be simplified as follows:
1. The chatter system is a linear one.Fig. 1 The main flow chart of this research
Fig. 2 Model of up milling
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2. The direction of dynamic cutting force is consistent
with that of the steady cutting force, and only the effectof cutting thickness is considered.
The initial dynamic equation can be established accord-
ing to the dynamic model in Fig. 4.
my
t cy
t ky t F t 1
where y(t) is the chatter displacement (mm), F(t) is the
dynamic cutting force (N), m is the modal mass of the chatter
system (Ns2/mm), c is the modal damp of the chatter system
(Ns/mm), and k is the modal stiffness of the chatter system
(Ns/mm).
Equation 1 is treated with Laplace transform. Thetransfer function matrix at the cutterworkpiece contact
zone is defined as follows:
6yy s y s
F s
1
k
1
swn
2 2xs
wn 1
2
where wn ffiffiffi
km
qis the natural pulsation of the chatter
system.
According to the automatic control theory, the time
domain characteristics of the chatter system depend on the
root of the characteristic equation of the transfer function.
When the real part of the root is zero, the system is the
critical state, and the root of characteristic equation can be
expressed as follows:
s iw 3
By substituting Eq. 3 with Eq. 2, the transfer function is
expressed as follows:
6yy iw 1
k
1 r2 i2xr
1 r2 2 2xr 24
where r wwn
, is the chatter pulsation, is the damping
ratio, and x c2mwn
.
On the basis of milling equations of Altinats and Budak,
the transfer function of chatter system is expressed as
follows.
6yy iw 4p
ZapKtayy 1 eiwT 5
where Z is the number of teeth, Kt is the tangential milling
force coefficient (N/mm2), ap is the axial depth of cutting
(mm), and yy is the directional dynamic milling coefficient
in the y direction and can be defined as follows:
ayy 1
2 cos 2f 2Krf Kr sin 2f
fexfst
6
where Kr is the radial milling force coefficient and st, ex
is the start and exit immersion angles of the cutter to andfrom the cutting zone, respectively. In the case of up
milling, the start immersion angle is zero, and the exit
immersion angle is ex. Then, the directional dynamic
milling coefficient can be expressed as follows:
ayy 1
21 cos2fex 2Krfex Kr sin2fex 7
Using the Eqs. 4 and 5, and the Eulers formula, the
axial stability limit is obtained as follows:
ap lim 2pk
ZKtayy
1 r2 2 2xr 2
1 r2
8
Here, the spindle speed ns corresponding to the axial
stability limit can be obtained with the following
expression:
ns 60w
Z 2mp p 2 arctan 2xrr21
9
where m is the whole number of full vibration cycles
between passages of two teeth.Fig. 4 Regenerative chatter model
Fig. 3 Workpiece in end milling
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2. Radial depth of cut
The start immersion angle of the cutter to the cutting
zone is zero, and the exit immersion angle of the cutter
from the cutting zone is ex. According to Fig. 2, therelationship between the radial depth of cut and exit angle
is defined as follows:
b=R 1 cos fex 10
where b is the radial depth of cutting (mm), and R is the
tool radius (mm).
2.2 Structure response model
Before stability and accuracy predictions can be made, the
dynamic parameters (natural frequency, damping ratio, and
stiffness) of the workpiece for each natural mode must be
developed. The most common method for testing the
dynamic parameters is to impact the structure with an
instrumented hammer and measure the system responsewith an accelerometer. The basic flow chart applied to test
the dynamic parameters is shown in Fig. 5.
Firstly, one needs to exert the exciting force on several
poi nts of the thi n-wal led plate and to mea sur e the
corresponding acceleration. Then, the transfer function be-
tween the impacted points and the measured points can be
obtained by the signal analysis equipment. Lastly, dynamic
parameters of chatter system are derived by curve fitting.
The size of the thin-walled plate used in this paper is
10010010 mm. The material of the part is aluminum
alloy with Youngs modulus of 70 Pa and Poissons ratio of
0.33. Through the developed method, the dynamic param-
eters of chatter system can be obtained. The natural
frequency is 502.5 rad/s, the damping ratio is 0.038, and
the stiffness is 4,500 N/mm.
2.3 Three-dimensional stability lobe
Through the cutting experiments, the tangential milling
force coefficient is 2,400 N/mm2, and the radial milling
force coefficient is 0.9 N/mm2. The cutter is a two-tooth
end-milling cutter. By using Matlab7.0 software, the
stability lobe in three-dimensional of the spindle speed,
axial, and radial depth of cut is represented in Fig. 6.
According to Fig. 6, when the radial depth is half of the
tool radius, the two-dimensional stability lobe diagram of
the axial depth and spindle speed is shown as Fig. 7. Thecurve in Fig. 7 is the boundary between chatter-free
machining operations and unstable process. According to
Fig. 5 Flow chart of testing the dynamic parameters Fig. 7 Two-dimensional stability lobe
Fig. 6 Three-dimensional stability lobe
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Fig. 7, one can select chatter-free combinations of machin-
ing parameters.According to Fig. 6, when the spindle speed is
10,000 rpm, the relationship between the axial and
radial depth under the condition of chatter-free is shown
as Fig. 8. The upper side of the curve in Fig. 8 is
unstable zone, and the down side of that is stable zone.
Figure 8 illustrates that the axial depth at the beginning
gradually decreases with the increment of the radial depth.
When the radial depth increases to a certain extent, the
axial depth begins to increase with the increment of the
radial depth. When the spindle speed is fixed, one can
select the appropriate parameters to avoid chatter accord-
ing to the curve in Fig. 8.
3 Material removal rate
Maximizing productivity is a primary goal in the machine
shop environment. For milling processes, this frequently
translates into maximizing the MRR. Possible mechanisms
for increasing MRR include increasing the spindle speed,
cutting depths, and feed rate. There are practical limits on
the spindle speed and feed rate at which a milling machine
can be operated. Therefore, the increasing MRR can be
achieved through increasing the cutting depth, the axial,
and radial depth of cut.
The mathematic equation for MRR can be expressed as
follows:
MRR ap b ns Z ft 11
0.0 0.2 0.4 0.6 0.8 1.00
2
4
6
8
10
MRR
(mm*rpm)
Radial depth / Tool radius
105
Fig. 9 Relationship between the radial depth and MRR
0.0 0.1 0.2 0.3 0.4 0.5 0.610
20
30
40
50
60
70
80
90
Exitimm
erseangle
Kr
Fig. 10 Relationship between the ex and Kr
Fig. 11 Relationship between MRR and ex
Fig. 8 Relationship between the axial and radial depth
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where ft is the feed per revolution per tooth. In general, the
effect of ft on stability is small and can be neglected [9].
Hence, MRR is proportional to the multiplication of the
axial and radial depth of cut, and the spindle speed. It is
interesting to find out at which combination of the axial and
radial depth of cut the spindle speed is fixed, where the
maximum value of MRR may be achieved. Therefore, a
normalized value of MRR is used hereafter.
MRRMRR
R ft Z ap
b
R ns 12
If the spindle speed is fixed at 10,000 rpm, at the
condition of chatter-free cutting for the milling of thin-
walled plate with two-tooth end milling, the relationship
between the radial depth and MRR is shown in Fig. 9.
Figure 9 illustrates that MRR is proportional to the radial
depth, and MRR is increased with the higher radial depth.
4 Maximum material removal rate of chatter-free
To obtain the maximum MRR, the radial depth should be
maximal. The acceptable (chatter-free) maximum radial
depth of cut depends on the geometry of the tool, the
direction of cutting, and the mode of milling (up or down
milling).
By substituting Eqs. 7, 8, and 10 with Eq. 12, the MRR
can be expressed as follows:
MRR4pkns
Kt
1 r2 2 2xr 2
1 r2
1 cos fex
1 cos 2fex 2Krfex Kr sin2fex 13
If the geometry and material of the tool, the material of
the workpiece, and the mode of the milling are made sure,
the milling force coefficients Kt and Kr will be certain.
According to the assumption (3) that the variation of
dynamic parameters due to the material removal is
neglected, the modal parameters k, , and r are invariant.
In order to obtain the maximum MRR of the chatter-free,
Eq. 13 is the computed derivatives of the exit immerse
angle ex; the differential equation can be obtained asfollows.
d MRR
dfex
4pkns
Kt
1 r2 2 2xr 2
1 r2
sin fex 1 cos 2fex 2Krfex Kr sin2fex 1 cos fex 2 sin 2fex 2Kr 2Kr cos2fex
1 cos2fex 2Krfex Kr sin2fex 2
14
Ifd MRR
dfex 0, the exit immerse angle ex can be
obtained. From Eq. 14, it is known that the exit immerse
angle is only related with the radial milling force coefficient
Kr. Through Matlab7.0, the exit immerse angle can be
obtained if Kr is made sure. That is to say, for a certain
cutting condition, one can select the appropriate ex to
obtain the maximum MRR of the chatter-free. The
relationship between the exit immerse angle and the radial
milling force coefficient Kr is shown as Fig. 10. Figure 10
illustrates that the exit immerse angle is increased with the
higher radial milling force coefficient. Consequently,
according to the three-dimensional stability lobe, one canobtain that the relationship between the maximum MRR of
the chatter-free and the exit immerse angle ex, which is
shown as Fig. 11. Figure 11 illustrates that the maximum
MRR of the chatter-free is increased with the larger exit
immerse angle ex.
5 Conclusions
Chatter has always been a significant problem in high-
speed machining, which is one of the major limitation on
productivity and part quality. In order to avoid chatter, one
needs to select the appropriate cutting parameters through
the stability lobe. In this paper, a three-dimensional stability
lobe theory has been presented. A three-dimensional, radial
depth of cut has been introduced in the stability lobe
diagram. This method is based on the identification of the
optimal pairs of axial and radial depth of cut. Thus, the
optimal cutting conditions for increased chatter-free MRRcan be obtained through the three-dimensional stability
lobe.
For the purpose of chatter avoidance, the primary
parameters are the axial and radial depth of the cut, which
are decisive in the productivity. Therefore, at the condition
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of stability cutting, one needs to select the optimal pairs of
axial and radial depth to obtain the maximum MRR. If the
geometry and material of the tool, the material of the
workpiece, and the mode of milling are made sure, the axial
and radial depth are both related with the exit immerse angle.
Therefore, in order to obtain the maximum MRR, one needs
to know the appropriate exit immerse angle. This paper
studies the relationship between the maximum MRR and exitimmerse angle, and finds that the maximum MRR of chatter-
free is increased with the larger exit immerse angle.
Acknowledgement The authors are grateful to the National High
Technology Research and Development Program of China for
supporting this work under grant no. 2008AA042405, the National
Natural Science Foundation of China for supporting this work under
grant no. 50675122, and National Science Foundation of Shandong of
China for supporting this work under grant no. Z2007F03.
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